EP3199848B1 - Kühlmittelsteuerventilvorrichtung - Google Patents

Kühlmittelsteuerventilvorrichtung Download PDF

Info

Publication number
EP3199848B1
EP3199848B1 EP17153001.7A EP17153001A EP3199848B1 EP 3199848 B1 EP3199848 B1 EP 3199848B1 EP 17153001 A EP17153001 A EP 17153001A EP 3199848 B1 EP3199848 B1 EP 3199848B1
Authority
EP
European Patent Office
Prior art keywords
rotor
seal member
refrigerant
port
diameter portion
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP17153001.7A
Other languages
English (en)
French (fr)
Other versions
EP3199848A1 (de
Inventor
Hideyuki Suzuki
Masanobu Matsusaka
Yojiro Koga
Naoto Yumisashi
Koichi Maruyama
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Aisin Corp
Original Assignee
Aisin Seiki Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Aisin Seiki Co Ltd filed Critical Aisin Seiki Co Ltd
Publication of EP3199848A1 publication Critical patent/EP3199848A1/de
Application granted granted Critical
Publication of EP3199848B1 publication Critical patent/EP3199848B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/08—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks
    • F16K11/087—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks with spherical plug
    • F16K11/0873—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks with spherical plug the plug being only rotatable around one spindle
    • F16K11/0876—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks with spherical plug the plug being only rotatable around one spindle one connecting conduit having the same axis as the spindle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
    • F16K5/06—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having spherical surfaces; Packings therefor
    • F16K5/061—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having spherical surfaces; Packings therefor knee-joint
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
    • F16K5/06—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having spherical surfaces; Packings therefor
    • F16K5/0663—Packings
    • F16K5/0689—Packings between housing and plug
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
    • F16K5/08—Details
    • F16K5/14—Special arrangements for separating the sealing faces or for pressing them together
    • F16K5/20—Special arrangements for separating the sealing faces or for pressing them together for plugs with spherical surfaces
    • F16K5/205—Sealing effected by the flowing medium
    • F16K5/208—Sealing effected by the flowing medium with tongue-shaped means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P2007/146—Controlling of coolant flow the coolant being liquid using valves

Definitions

  • This disclosure relates to a refrigerant control valve device which controls a flow of a refrigerant by the rotation of a rotor.
  • JP 2013-29127A discloses a refrigerant control valve device (a valve device in Reference 1) in which a valve body is rotatably accommodated in a valve housing, and the refrigerant control valve device includes a ring-shaped seal body (a seal member in Reference 1), which is inserted from the outside into a cylindrical portion of a guide member that constitutes a refrigerant flow path, and a spring member which biases the seal body in a direction where the seal body comes into contact with the outer surface of the valve body.
  • the valve body has a spherical outer surface, and the seal body is formed in a ring shape so as to come into contact with the outer surface.
  • a communication portion is formed on the outer circumferential surface of the seal body so as to apply the pressure of the refrigerant to a pressure receiving surface of the seal body facing a valve body, and a pressure receiving surface opposite to the pressure receiving surface.
  • the respective pressure receiving surfaces have the same area and forming the communication portion, the pressure applied to the pressure receiving surface from the refrigerant in a direction opposite to the biasing force of the spring member and the pressure applied to the pressure receiving surface from the refrigerant in a direction along the biasing force of the spring member cancel out each other, thereby inhibiting a trouble that a pressure is excessively applied to the seal body.
  • a predetermined pressure is applied to the pair of pressure receiving surfaces from the refrigerant when the valve body is in an opened posture.
  • the refrigerant is not supplied into the space in which the valve body is accommodated when the valve body is in a closed posture, there is concern that the pressure applied to the pair of pressure receiving surfaces from the refrigerant may be temporarily unbalanced when the valve body is operated.
  • the thermal management module for controlling fluid flows of at least one fluid circuit of a cooling or lubricating system of an internal combustion engine.
  • the thermal management module comprises a module housing with a plurality of fluid ports through which fluid can interact with openings of a rotary valve integrated in the module housing.
  • US 2,837,308 discloses fluid control valves such as plug cocks of the kind having the joint between the obturating member and the body of the valve made by means of at least one seating ring supported against the obturating member by a flexible diaphragm sealed to the obturating member and sealed at its periphery within the body and exposed on its outer surface to fluid pressure.
  • a feature of a refrigerant control valve device resides in that the refrigerant control valve device includes: a spherical rotor having an opening opened in a direction of a rotation axis, and configured to rotate about the rotation axis; a housing which includes at least one circumferential port configured to be formed around an axis passing through a spherical center of the rotor, and an axial port formed at a side of the opening in the direction of the rotation axis, in which the housing is configured to allow a refrigerant to flow therein and the rotor is accommodated in the housing; at least one hole formed in the rotor and configured to allow the internal space of the rotor and the circumferential port to communicate with each other when the rotor rotates; a ring-shaped seal member installed coaxially with the circumferential port, and accommodated in the housing to be abutted on an outer surface of the rotor; a biasing member configured to apply a biasing force
  • the seal member includes a first pressure receiving surface configured to receive a pressure applied from the refrigerant in a direction identical to a biasing direction of the biasing member, and a second pressure receiving surface having an area that is substantially equal to that of the first pressure receiving surface, and configured to receive a pressure applied by the refrigerant in a direction opposite to the biasing direction with respect to the seal member, at a side of the seal member which is filled with the refrigerant when the rotor is in a state in which the internal space of the rotor and the circumferential port do not communicate with each other.
  • the pressure of the refrigerant applied in a direction identical to the biasing direction of the biasing member and the pressure of the refrigerant applied in a direction opposite to the biasing direction are cancelled out, at a side of the seal member which is filled with the refrigerant, for example, even when the rotor is operated. Therefore, since only the biasing force of the biasing member may be applied to the seal member, it is possible to improve a sealing property between the seal member and the rotor.
  • the refrigerant control valve device having the present configuration may be used under various environments.
  • the axial port is used as an intake port which becomes an inlet side of a coolant and the circumferential port is used as a discharge port which becomes an outlet side of the coolant
  • the axial port side is at a higher pressure
  • the circumferential port side is at a lower pressure
  • the relationship between the intake port and the discharge port is reversed, so that the axial port side is at a lower pressure and the circumferential port side is at a higher pressure.
  • the packing body is disposed to form the first pressure receiving surface and the second pressure receiving surface that define substantially the same area when viewed in a biasing direction of the biasing member at a side of the seal member which is filled with the refrigerant, the sealing property can be stably secured. That is, the sealing property can be improved to correspond to the method of using the refrigerant control valve device having the present configuration (a pressure relationship of the refrigerant, and a flow direction of the refrigerant).
  • the housing includes: a cylindrical holder that includes a large diameter portion that accommodates the biasing member, a small diameter portion that has a smaller diameter than the large diameter portion and is inserted into an inner diameter portion of the seal member, and a stepped portion that connects the large diameter portion and the small diameter portion.
  • the central axis of the biasing member and the central axis of the seal member may be further aligned to be coaxial. Therefore, the assembly precision of the biasing member and the seal member can be improved, and the biasing force of the biasing member can be precisely applied to the seal member. Therefore, the sealing property between the seal member and the rotor can be improved.
  • the packing body has a convex portion that extends toward at least one of a circumferential port side and a rotor side.
  • the convex portion is formed to extend toward the rotor, and when the refrigerant flows from the circumferential port side to the rotor side, the convex portion is formed to extend toward the circumferential port side.
  • the convex portion acts to be pressed against the seal member with respect to a flow (pressure) of the refrigerant such that the sealing property between the packing body and the seal member can be further improved.
  • Another feature of the aspect of this disclosure resides in that a position at which a virtual cylindrical surface obtained by extending an outer circumferential surface of the large diameter portion of the holder in a direction along an axis of the holder intersects an outer surface of the rotor is set to a position at which the seal member and the outer surface of the rotor come into contact with each other.
  • another feature of the aspect of this disclosure resides in that the packing body is abutted on the seal member on the virtual cylindrical surface of the holder.
  • the refrigerant control valve device V is provided in an engine cooling circuit O illustrated in Fig. 1 , and includes an axial port PS that receives a coolant (e.g., refrigerant) from an engine E as an internal combustion engine for a vehicle, a first circumferential port U1 that sends the coolant to a radiator R through a radiator hose 1, and a second circumferential port U2 that sends the coolant to a heater core H through a heater hose 2.
  • the engine E includes a cylinder head part Ea and a cylinder block part Eb, and the coolant is supplied from the cylinder head part Ea to the axial port PS of the refrigerant control valve device V.
  • the coolant supplied to the radiator R and the coolant supplied to the heater core H are sent to a water pump (W/P) 6 from an inlet valve 7, and return back to the cylinder block part Eb of the engine E from the water pump 6.
  • W/P water pump
  • the coolant is supplied from the refrigerant control valve device V to the radiator R and the heater core H.
  • the coolant may be supplied and used for heat exchange of, for example, engine oil or a fluid of an automatic transmission.
  • a third circumferential port may be formed for the refrigerant control valve device V.
  • the refrigerant control valve device V includes a resin-made housing A, a resin-made rotor 3 that is accommodated in the housing A to be rotatable about a rotation axis X and has a spherical outer surface 31 (outer wall surface), and a controller B that rotates the rotor 3 through a rotating shaft 2 (e.g., a shaft).
  • a first seal 22 and a second seal 23, into which the shaft 2 is inserted to be rotatable around the rotation axis X of the shaft 2 are disposed to seal a portion between the rotor 3 and the controller B.
  • a spacer 24 is provided between the first seal 22 and the second seal 23 in order to secure a space between the spacer 24 and each of the seals.
  • a housing body 10 is formed with a communication path (not illustrated) that communicates with a drain hole (not illustrated) that allows the space in which the spacer 24 is provided and the outside (atmosphere) to communicate with each other.
  • the refrigerant control valve device V is configured to supply the coolant of the engine E to at least one of the radiator R and the heater core H as a device that requires heat, and to make a state in which no coolant is supplied to any of the radiator R and the heater core H.
  • the rotation axis X is set to be orthogonal to an opening plane of the axial port PS from a center position of the axial port PS.
  • the axial port PS is formed at one side in the axial direction of the housing body 10 of the housing A.
  • the housing A is formed with: a circumferential port US (e.g., a first circumferential port U1) having a cylindrical sleeve unit 11 (e.g., a first sleeve unit) protruding outward; and a second circumferential port U2 (illustrated in Fig. 1 but not illustrated in Fig. 2 ) having a second sleeve unit (not illustrated) protruding outward.
  • an inner diameter of the first sleeve unit 11 is larger than an inner diameter of the second sleeve unit.
  • the first circumferential port U1 and the second circumferential port U2 are members made of the same material, and have the same function.
  • the first circumferential port U1 includes a cylindrical first sleeve unit 11 to which the radiator hose 1 is connected, a first flange unit 12 formed in a flange shape on the outer circumference of the first sleeve unit 11, and a seal mechanism 4 (e.g., a first seal mechanism) which is accommodated in an inner diameter portion 10a of the housing body 10.
  • a seal mechanism 4 e.g., a first seal mechanism
  • the first flange unit 12 is connected with the housing body 10 over the entire outer circumference thereof by welding.
  • first flange unit 12 may be connected with the housing body 10 by being fastened thereto by bolts (not illustrated) or the like.
  • first seal mechanism 4 includes an annular first seal member 41, a first packing body 42, a first holder 43, a first biasing member 44, and a first fixing member 45. These components are provided in a state of being inserted into the inner diameter portion 10a of the housing body 10 which extends in a direction of the first sleeve unit 11.
  • the rotor 3 includes a rotor main body 30 that rotates integrally with the shaft 2 that rotates about the rotation axis X.
  • the shaft 2 is retained by a bearing unit 21 formed in the housing body 10.
  • the bearing unit 21 is formed to extend to a position (the axial port PS side illustrated in Fig. 2 ) below a wall center T where a first centerline Q1 of the first sleeve unit 11 and the rotation axis X intersect.
  • the rotor main body 30 includes an opening 33 as a receiving portion that receives the coolant from the axial port PS opened in the direction along the rotation axis X, an inner wall 35 of the rotor 3 which is connected to the opening 33 and forms an internal space 34 therein, an outer wall surface 31 which is formed in a spherical shape around the wall center T, and a control hole 32 (a specific example of a hole) which is formed in the outer wall surface 31 so as to send the coolant from the internal space 34 of the rotor 3 to the first circumferential port U1 or the second circumferential port U2.
  • an opened portion 36 is formed at a side opposite to the opening 33 in a state in which the shaft 2 penetrates the opened portion 36.
  • Plural connecting bodies 37 which are formed at a protruding end of the shaft 2, are connected to the inner wall 35 of the rotor 3 of the rotor main body 30, so that the plural connecting bodies 37 are rotated integrally with the rotor 3.
  • the opened state refers to a state in which as the rotor 3 is rotated, the coolant flows to at least a part of the control hole 32, and the internal space 34 and the circumferential port PS communicate with each other.
  • the completely closed state refers to a state in which, as the rotor 3 is rotated, the outer wall surface 31 of the rotor 3 blocks the internal space 34 and the circumferential port US, and thus the coolant does not flow therethrough.
  • the interior of the housing body 10 is filled with the coolant.
  • the opening area of the opening 33 of the rotor 3 at the axial port PS side is necessarily greater than an opening area formed by the control hole 32 and the first seal mechanism 4, and as a result, the interior of the housing body 10 is always filled with the coolant.
  • the coolant does not flow to the circumferential port US, and thus the interior of the housing body 10 is always filled with the coolant.
  • the coolant (F1 portion illustrated in Fig. 3 ) in the housing body 10 may leak to the circumferential port US from the outer diameter of the first seal member 41 installed in the first seal mechanism 4, but the leak of the coolant is inhibited by installing a packing body 42 to be described below.
  • the first seal mechanism 4 serves to cut off a flow of the coolant between the first circumferential port U1 and the outer wall surface 31 of the rotor 3 since the entire circumference of the first seal mechanism 4 comes into close contact with the spherical outer wall surface 31 when the rotor 3 is set to a posture that closes the first circumferential port U1.
  • the first seal member 41 is formed in an annular shape and made of a flexible resin such as polytetrafluoroethylene (PTFE).
  • the first seal member 41 is movable along the first centerline Q1 of the first sleeve unit 11.
  • the first seal member 41 includes an inner diameter portion 41a into which the first holder 43 is inserted, a curved portion 41b which is abutted on the outer wall surface 31 of the rotor 3, and an outer diameter portion 41c which is slidably abutted on the first packing body 42.
  • the first seal member 41 forms a first pressure receiving surface S1 that receives pressure applied by the refrigerant in a direction identical to the biasing direction of the first biasing member 44, and a second pressure receiving surface S2 that receives pressure applied by the refrigerant in a direction opposite to the biasing direction of the first biasing member 44.
  • the first pressure receiving surface S1 and the second pressure receiving surface S2 are formed as the first packing body 42 to be described below is disposed to have substantially the same area when viewed in the biasing direction of the first biasing member 44.
  • the first packing body 42 is disposed to be abutted on the outer diameter potion 41c of the first seal member 41 which is formed on the virtual cylindrical surface I1 of the first holder 43.
  • the first packing body 42 is formed in an annular shape and made of flexible resin, and has an insertion portion 42c formed to be assembled to the housing body 10.
  • the insertion portion 42c is provided in a state of being inserted into the inner diameter portion 12 of the housing body10.
  • a convex portion 42a on which the outer diameter portion 41c of the first seal member 41 is slidably abutted is provided on an inner diameter portion of the first packing body 42.
  • the convex portion 42a is formed to extend toward the rotor 3 side.
  • the first seal member 41 is configured to be movable along the first centerline Q1, but the first packing body 42 is retained not to be moved by being held by an abutment surface 45a of the first fixing member 45 and an abutment surface 13a of the housing body 10.
  • the convex portion 42a is formed to extend toward the rotor 3 side, the convex portion 42a acts to be pressed against the outer diameter portion 41c of the first seal member 41 even though the axial port PS side is a high pressure, thereby inhibiting the coolant from leaking from a gap between the first packing body 42 and the first seal member 41.
  • the first holder 43 is made of a highly rigid metal or resin, and inserted into the inside of the first seal member 41. Further, the first holder 43 is formed to accommodate the first biasing member 44.
  • the first holder 43 is a cylindrical member formed around the first centerline Q1, and has a small diameter portion 43c which has a smaller diameter at a side of the first seal member 41 than at a side of the first biasing member 44, a large diameter portion 43b which has a larger diameter at the side of the first biasing member 44 than at the side of the first seal member 41, and a stepped portion 43a which connects the small diameter portion 43c and the large diameter portion 43b.
  • the stepped portion 43a is formed such that one side of the stepped portion 43a is abutted on the first biasing member 44 so that the biasing force is applied thereto, and the other side of the stepped portion 43a is abutted on an end portion of the first seal member 41.
  • the virtual cylindrical surface 11 which extends in a direction along the first centerline Q1 of the outer diameter of the large diameter portion 43b of the first holder 43, is set to be abutted on the first seal member 41 and the outer wall surface 31 of the rotor 3.
  • the first pressure receiving surface S1 which receives a hydraulic pressure in the biasing direction of the first biasing member 44, has the same area as the second pressure receiving surface S2 which receives a hydraulic pressure in a direction opposite to the biasing direction of the first biasing member 44.
  • the hydraulic pressure applied to the first seal member 41 may stably maintain a pressure balance in the first refrigerant control valve device V such that the first seal member 41 and the outer wall surface 31 of the rotor 3 may be stably abutted on each other. Therefore, the sealing property may be stably maintained over a long period of time.
  • a position where the first seal member 41 and the outer wall surface 31 of the rotor 3 are abutted on each other does not have to be exactly coincident with the virtual cylindrical surface 11, and some errors may be included because the abutment is to cancel out the pressure applied from the coolant.
  • a first spring 44 which is the first biasing member, is made of a metallic material, and disposed at a position where one end of the first spring 44 is abutted on the first holder 43, and the other end of the first spring 44 is abutted on the first fixing member 45. With the biasing force of the first spring 44, the first seal member 41 is in contact with the outer wall surface 31 of the rotor 3. In addition, the first spring 44 does not protrude toward the first circumferential port U1 by the first fixing member 45.
  • the first centerline Q1 which is the center of the first sleeve unit 11, is inclined with respect to the rotation axis X.
  • the first centerline Q1 intersects the rotation axis X, the position where the first centerline Q1 intersects the rotation axis X is the wall center T, and the wall center T is coincident with the center of the spherical outer wall surface 31 of the rotor 3.
  • the direction in which the first centerline Q1 is inclined is set such that an outer end side of the first sleeve unit 11 is spaced apart from the rotation axis X and spaced apart from the axial port PS to the extent of a downstream side in a direction in which the coolant flows in the first sleeve unit 11.
  • the second circumferential port U2 is also formed to have the same configuration and the same material as the first circumferential port U1, but the second circumferential port U2 may not be the same as the first circumferential port U1 in terms of size.
  • the controller B includes a wheel gear 51 that is provided at an end portion of the shaft 2, a worm gear 52 that is engaged with the wheel gear 51, a motor 55 that rotates the worm gear 52, a magnet (not illustrated) that rotates integrally with the wheel gear 51, and a non-contact type rotation angle sensor 53 that detects a rotation posture of the rotor 3 by detecting a magnetic field that changes as the magnet rotates.
  • the control device sets a target posture of the rotor 3 based on a detection result of a water temperature sensor that measures the temperature of the coolant of the engine E or based on information required for the heater core H, and performs a control based on a detection signal from the rotation angle sensor 53 such that the rotation posture of the rotor 3 becomes the target posture.
  • the controller B implements a control of setting a rotation posture of the rotor 3 to a completely opened posture in which the first circumferential port U1 and the second circumferential port U2 are simultaneously opened, a first opened posture in which only the first circumferential port U1 is opened, a second opened posture in which only the second circumferential port U2 is opened like the first opened posture, and a completely closed posture in which the first circumferential port U1 and the second circumferential port U2 are closed.
  • the first circumferential port U1 and the second circumferential port U2 communicate with the internal space 34, and the coolant is supplied to the radiator R from the first circumferential port U1, and at the same time, the coolant is supplied to the heater core H from the second circumferential port U2.
  • the first circumferential port U1 and the internal space 34 communicate with each other, and as a result, the coolant may be supplied only to the radiator R.
  • the second circumferential port U2 and the internal space 34 communicate with each other, and as a result, the coolant may be supplied only to the heater core H.
  • both of the first circumferential port U1 and the second circumferential port U2 are in a non-communicating state with the internal space 34, and as a result, the coolant is not supplied to the radiator R and the heater core H.
  • the completely closed posture is set in a case in which early warm air is required, for example, immediately after the engine E starts.
  • the first seal member 41 is in close contact with the outer wall surface 31 of the rotor 3, and a second seal member (not illustrated) is also in close contact with the outer wall surface 31 of the rotor 3.
  • controller B is configured to perform a control to arbitrarily set a supply amount of the coolant to a state in which both of the first circumferential port U1 and the second circumferential port U2 restrict the flow of the coolant (a state in which both of the first circumferential port U1 and the second circumferential port U2 are not completely opened) by setting the rotation posture of the rotor 3.
  • the second embodiment uses a refrigerant control valve device V having a configuration that is in common with that of the first embodiment, but because the refrigerant control valve device V is used for an engine cooling circuit O illustrated in Fig. 4 , the flow direction of the coolant in the refrigerant control valve device V is opposite to that in the first embodiment, and the configuration of the seal mechanism 4 is different from that in the first embodiment.
  • reference numerals in common with those in the first embodiment are assigned.
  • the refrigerant control valve device V is provided in the engine cooling circuit O illustrated in Fig. 4 , and includes an axial port PS that returns the coolant to an engine E from the engine E as an internal combustion engine for a vehicle, a first circumferential port U1 that is supplied with the coolant of a radiator R through a radiator hose 1, and a second circumferential port U2 that is supplied with the coolant of a heater core H through a heater hose 2.
  • the engine E has a cylinder head part Ea and a cylinder block part Eb, and the coolant is supplied from the cylinder head part Ea to an outlet valve 5.
  • the outlet valve 5 is configured to be able to split the flow of coolant into a flow directed to the radiator R and a flow directed to the heater core H.
  • the coolant from the axial port PS is sent to a water pump (W/P) 6, and returns back to the cylinder block part Eb of the engine E from the water pump 6.
  • the refrigerant control valve device V controls the coolant from the radiator R and the heater core H and returns the coolant back to the engine E.
  • a third inlet port may be formed for the refrigerant control valve device V configured to receive the coolant from a device that performs heat exchange of the engine oil or the fluid.
  • the axial port PS is formed at one side in the axial direction of a housing body 10 of the housing A.
  • the housing A is formed with: a circumferential port US (e.g., first circumferential port U1) having a cylindrical sleeve unit 11 (e.g., a first sleeve unit) protruding outward, and a second circumferential port U2 (illustrated in Fig. 4 but not illustrated in Fig. 5 ) having a second sleeve unit (not illustrated) protruding outward.
  • the inner diameter of the first sleeve unit 11 is larger than the inner diameter of the second sleeve unit.
  • the first circumferential port U1 and the second circumferential port U2 are members made of the same material, and have the same function.
  • the first circumferential port U1 includes a cylindrical first sleeve unit 11 to which the radiator hose 1 is connected, a first flange unit 12 which is formed in a flange shape on the outer circumference of the first sleeve unit 11, and the seal mechanism 4 (e.g., a first seal mechanism) which is accommodated in an inner diameter portion 10a of the housing body 10.
  • the seal mechanism 4 e.g., a first seal mechanism
  • the first flange unit 12 is connected with the housing body 10 over the entire outer circumference thereof by welding.
  • first flange unit 12 may connected with the housing body 10 by being fastened thereto by bolts (not illustrated) or the like.
  • first seal mechanism 4 includes an annular first seal member 41, a first packing body 42, a first holder 43, a first spring 44, and a first fixing member 45. These components are provided in a state of being inserted into the inside of the inner diameter portion 10a of the housing body 10 which extends in a direction of the first sleeve unit 11.
  • a member that is the same as and corresponds to that in the first embodiment is used, and the rotors 3 have the same function as that of the first embodiment.
  • a difference from the first embodiment is that the circumferential port US (F2 side illustrated in Fig. 5 ) is always filled with the coolant when the rotor 3 is in the opened posture and in the completely closed posture.
  • the first seal mechanism 4 serves to cut off a flow of the coolant between the first circumferential port U1 and an outer wall surface 31 of the rotor 3 since the entire circumference of the first seal mechanism 4 comes into close contact with the spherical outer wall surface 31 when the rotor 3 is set to a posture that closes the first circumferential port U1.
  • first seal member 41 the first holder 43, and the first spring 44 have the same configuration and material as those in the first embodiment, descriptions thereof will be omitted.
  • a hydraulic pressure which is different from the hydraulic pressure applied to the first seal member 41 in the first embodiment, is applied.
  • the first seal member 41 forms a first pressure receiving surface S1 which receives a pressure applied by the refrigerant in a direction identical to the biasing direction of a first biasing member 44, and a second pressure receiving surface S2 which receives a pressure applied by the refrigerant in a direction opposite to the biasing direction of the first biasing member 44.
  • the first pressure receiving surface S1 and the second pressure receiving surface S2 are formed as the first packing body 42 is disposed to have substantially the same area when viewed in the biasing direction of the first biasing member 44.
  • the first seal member 41 when the first seal member 41 is abutted on the rotor 3 on an extension line of a virtual cylindrical surface I1 of the first holder 43, the first packing body 42 is disposed to be abutted on an outer diameter potion 41c of the first seal member 41 which is formed on the virtual cylindrical surface I1 of the first holder 43. Therefore, a pressure balance in the first refrigerant control valve device V may be stably maintained, and the first seal member 41 may be stably abutted on the outer wall surface 31 of the rotor 3.
  • the first packing body 42 is formed in an annular shape and made of flexible resin, and has an insertion portion 42c formed to be assembled to the housing body 10.
  • the insertion portion 42c is provided in a state of being inserted into a reduced diameter portion 13 of the housing body10.
  • the first packing body 42 includes a convex portion 42b (illustrated in Fig. 5 ) on which the inner diameter portion of the first packing body 42 and the outer diameter portion 41c (illustrated in Fig. 5 ) of the first seal member 41 are slidably abutted.
  • the convex portion 42b is formed to extend toward the entrance side of the first circumferential port U1.
  • the first seal member 41 is configured to be movable along the first centerline Q1, but the first packing body 42 is retained not to be moved by being held by an abutment surface 45a of the first fixing member 45 and an abutment surface 13a of the housing body 10.
  • the convex portion 42a is formed to extend toward the entrance side of the first circumferential port U1
  • the convex portion 42b acts to be pressed against the outer diameter portion 41c of the first seal member 41 even though the first circumferential port U1 side is at a high pressure, thereby inhibiting the coolant from leaking from a gap between the first packing body 42 and the first seal member 41.
  • controller B a member that is the same as and corresponds to the controller B in the first embodiment is used, and the controller B has the same function as that of the first embodiment.
  • the electric controller C implements a control of setting a rotation posture of the rotor 3 to a completely opened posture in which the first circumferential port U1 and the second circumferential port U2 are simultaneously opened, a first opened posture in which only the first circumferential port U1 is opened, a second opened posture in which only the second circumferential port U2 is opened like the first opened posture, and a completely closed posture in which the first circumferential port U1 and the second circumferential port U2 are closed.
  • the first circumferential port U1 and the second circumferential port U2 communicate with the internal space 34 such that the coolant may return back to the engine E from the radiator R and the heater core H.
  • the first circumferential port U1 and the internal space 34 communicate with each other, and as a result, the coolant may return back to the engine E from the radiator R.
  • the second circumferential port U2 and the internal space 34 communicate with each other, and as a result, the coolant may return back to the engine E from the heater core H.
  • both of the first circumferential port U1 and the second circumferential port U2 are in a non-communicating state with the internal space 34, and as a result, the coolant does not return back to the engine E from the radiator R and the heater core H.
  • the completely closed posture is set in a case in which early warm air is required, for example, immediately after the engine E starts.
  • the controller B is configured to perform a control operation of arbitrarily setting a supply amount of the coolant to a state in which both of the first circumferential port U1 and the second circumferential port U2 restrict a flow of the coolant (a state in which both of the first circumferential port U1 and the second circumferential port U2 are not completely opened), by setting the rotation posture of the rotor 3.
  • the third embodiment uses a refrigerant control valve device V having a configuration that is in common with those of the first and second embodiments, but is different from those of the first and second embodiments in that a seal mechanism 4 is configured to be used for the engine cooling circuit O illustrated in Figs. 1 and 4 regardless of a flow direction of the coolant.
  • a seal mechanism 4 is configured to be used for the engine cooling circuit O illustrated in Figs. 1 and 4 regardless of a flow direction of the coolant.
  • reference numerals in common with those in the first and second embodiments are assigned.
  • the refrigerant control valve device V may be applied to both of the engine cooling circuits O disclosed in the first and second embodiments.
  • the third embodiment has the same use application or the same function as the first and second embodiments, a description thereof will be omitted.
  • a packing body 42 which is different from those in the first and second embodiments, will be described in detail.
  • the packing body 42 (e.g., the first packing body illustrated in Fig 6 ) is formed in an annular shape and made of a flexible resin, and has an insertion portion 42c formed to be assembled to the housing body 10.
  • the insertion portion 42c is provided in a state of being inserted into a reduced diameter portion 13 of the housing body10.
  • the packing body 42 includes plural convex portions 42a and 42b on which an inner diameter portion of the first packing body 42 and an outer diameter portion 41c of the first seal member 41 are slidably abutted.
  • the convex portions 42a and 42b are formed to extend toward the rotor 3 side, and toward the entrance side of the first circumferential port U1.
  • the first seal member 41 is configured to be movable along the first centerline Q1, but the first packing body 42 is retained not to be moved by being held by an abutment surface 45a of the first fixing member 45 and an abutment surface 13a of the housing body 10.
  • the convex portions 42a and 42b act to be pressed against the outer diameter portion 41c of the first seal member 41 even though both of the axial port PS side and the first circumferential port U1 side are at a high pressure, thereby inhibiting the coolant from leaking from a gap between the first packing body 42 and the first seal member 41.
  • the flow rate control valve device disclosed here may be used for various objects to be cooled in various types of vehicles.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Taps Or Cocks (AREA)
  • Multiple-Way Valves (AREA)
  • Sliding Valves (AREA)

Claims (3)

  1. Kühlmittelsteuerventilvorrichtung (V) mit:
    einem sphärischen Rotor (3), der eine Öffnung (33), die in einer Richtung einer Drehachse (X) geöffnet ist, aufweist und zur Drehung um die Drehachse ausgebildet ist;
    einem Gehäuse (A), das mindestens eine Umfangsöffnung (US, US1, US2), die so ausgebildet ist, dass sie um eine Achse, die durch ein sphärisches Zentrum des Rotors geht, ausgebildet ist, und eine axiale Öffnung (PS), die auf einer Seite der Öffnung in der Richtung der Drehachse ausgebildet ist, aufweist, wobei das Gehäuse so ausgebildet ist, dass ein Kühlmittel darin strömen kann, und der Rotor in dem Gehäuse aufgenommen ist;
    mindestens einem Loch (32), das in dem Rotor ausgebildet ist und dazu ausgebildet ist, zu ermöglichen, dass der Innenraum des Rotors und die Umfangsöffnung miteinander in Verbindung stehen können, wenn sich der Rotor dreht;
    einem ringförmigen Dichtungsbauteil (41), das koaxial mit der Umfangsöffnung eingebaut ist und so in dem Gehäuse aufgenommen ist, dass es an einer Außenfläche des Rotors anliegt;
    einem Vorbelastungsbauteil (44), das zum Aufbringen einer Vorbelastungskraft auf das Dichtungsbauteil in einer Richtung zu dem sphärischen Zentrum des Rotors ausgebildet ist;
    einem Abdichtkörper (42), der zwischen dem Gehäuse und einem Außendurchmesserteil (41c) des Dichtungsbauteils vorgesehen ist und so ausgebildet ist, dass er verschiebbar an dem Außendurchmesserteil des Dichtungsbauteils anliegt; und
    einem Befestigungsbauteil (45), das zum Halten des Abdichtkörpers mit dem Gehäuse in einer Richtung, in der sich die Umfangsöffnung erstreckt, ausgebildet ist,
    dadurch gekennzeichnet, dass
    das Dichtungsbauteil eine erste Druckaufnahmefläche (S1), die zum Aufnehmen eines Drucks, der von dem Kühlmittel in einer Richtung, die identisch mit einer Vorbelastungsrichtung des Vorbelastungsbauteils ist, aufgebracht wird, ausgebildet ist, und eine zweite Druckaufnahmefläche (S2), die eine Fläche, die im Wesentlichen gleich der der ersten Druckaufnahmefläche ist, aufweist und zum Aufnehmen eines Drucks, der durch das Kühlmittel in einer Richtung entgegengesetzt zu der Vorbelastungsrichtung in Bezug auf das Dichtungsbauteil aufgebracht wird, ausgebildet ist, aufweist, auf einer Seite des Dichtungsbauteils, die mit dem Kühlmittel gefüllt ist, wenn sich der Rotor in einem Zustand befindet, in dem der Innenraum des Rotors und die Umfangsöffnung nicht miteinander in Verbindung stehen,
    bei der das Gehäuse einen zylindrischen Halter (43) aufweist, der einen Teil (43b) mit großem Durchmesser, der das Vorbelastungsbauteil aufnimmt, einen Teil (43c) mit kleinen Durchmesser, der einen kleineren Durchmesser als der Teil mit großem Durchmesser aufweist und in einen Innendurchmesserteil (41a) des Dichtungsbauteils eingeführt ist, und einen abgestuften Teil (43a), der den Teil mit großem Durchmesser und den Teil mit kleinem Durchmesser verbindet, aufweist,
    bei der eine Position, an der eine virtuelle zylindrische Fläche (I1), die durch Verlängern einer Außenumfangsfläche des Teils mit großem Durchmesser des Halters in einer Richtung entlang einer Achse des Halters erhalten wird, eine Außenfläche des Rotors schneidet, auf eine Position eingestellt ist, an der das Dichtungsbauteil und die Außenfläche des Rotors in Kontakt miteinander kommen, und
    bei der der Abdichtkörper auf der virtuellen zylindrischen Fläche an dem Dichtungsbauteil anliegt.
  2. Kühlmittelsteuerventilvorrichtung nach Anspruch 1, bei der auf einer Seite, auf der der Abdichtkörper an dem Dichtungsbauteil anliegt, der Abdichtkörper einen konvexen Teil aufweist, der sich zu mindestens einer von einer Umfangsöffnungsseite und einer Rotorseite erstreckt.
  3. Kühlmittelsteuerventilvorrichtung nach Anspruch 2, bei der, wenn das Kühlmittel von der Rotorseite zu der Umfangsöffnungsseite strömt, der konvexe Teil so ausgebildet ist, dass er sich zu dem Rotor erstreckt, und wenn das Kühlmittel von der Umfangsöffnungsseite zu der Rotorseite strömt, der konvexe Teil so ausgebildet ist, dass er sich zu der Umfangsöffnungsseite erstreckt.
EP17153001.7A 2016-01-26 2017-01-25 Kühlmittelsteuerventilvorrichtung Active EP3199848B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2016012030A JP6668780B2 (ja) 2016-01-26 2016-01-26 冷媒制御バルブ装置

Publications (2)

Publication Number Publication Date
EP3199848A1 EP3199848A1 (de) 2017-08-02
EP3199848B1 true EP3199848B1 (de) 2020-02-19

Family

ID=57944274

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17153001.7A Active EP3199848B1 (de) 2016-01-26 2017-01-25 Kühlmittelsteuerventilvorrichtung

Country Status (4)

Country Link
US (1) US10513966B2 (de)
EP (1) EP3199848B1 (de)
JP (1) JP6668780B2 (de)
CN (1) CN107023375A (de)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017213777B4 (de) * 2017-08-08 2022-02-17 Audi Ag Verfahren zum Betreiben einer Antriebseinrichtung eines Kraftfahrzeugs mit mehreren Kühlmittelkühlern sowie entsprechende Antriebseinrichtung
KR102359946B1 (ko) * 2017-09-08 2022-02-07 현대자동차 주식회사 냉각수 제어밸브 유닛의 제어방법
DE102018122923A1 (de) * 2017-09-20 2019-03-21 Mikuni Corporation Drehventilvorrichtung
JP6940347B2 (ja) * 2017-09-20 2021-09-29 株式会社ミクニ ロータリ式バルブ装置
JP7136626B2 (ja) * 2018-08-21 2022-09-13 株式会社ミクニ ロータリ式バルブ装置
JP7101544B2 (ja) * 2018-06-06 2022-07-15 日立Astemo株式会社 制御弁
JP7146540B2 (ja) * 2018-09-13 2022-10-04 株式会社山田製作所 制御バルブ
DE202018105534U1 (de) * 2018-09-26 2018-10-04 Johnson Electric Germany GmbH & Co. KG Ventil
DE112020000356T5 (de) * 2019-01-08 2021-11-04 Zhejiang Yinlun Machinery Co., Ltd. Doppeldichtstruktur eines Elektroventils, Dichtstruktur eines Elektroventils, und Elektroventil statischer Dichtstruktur
JP7192546B2 (ja) * 2019-02-07 2022-12-20 株式会社デンソー 冷却水制御弁装置
JP7172749B2 (ja) * 2019-03-06 2022-11-16 株式会社デンソー バルブ装置
CN111365113A (zh) * 2020-03-26 2020-07-03 重庆长安汽车股份有限公司 发动机冷却系统热管理模块及发动机冷却系统
JP2022025340A (ja) * 2020-07-29 2022-02-10 株式会社ミクニ ロータリ式バルブ装置
JP2022057185A (ja) * 2020-09-30 2022-04-11 Ntn株式会社 流量制御バルブ用シールおよび流量制御バルブ装置
KR102577720B1 (ko) * 2021-10-19 2023-09-12 지엠비코리아 주식회사 밸브 장치
JP2023067563A (ja) 2021-11-01 2023-05-16 日本サーモスタット株式会社 循環回路部材、及び循環回路部材の製造方法

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2751185A (en) * 1948-02-13 1956-06-19 Saunders Valve Co Ltd Seat for rotary spherical plug valve
US2837308A (en) * 1955-06-06 1958-06-03 Saunders Valve Co Ltd Fluid control valves
GB848151A (en) * 1958-06-24 1960-09-14 Neue Argus Gmbh Stopcock with spherical plug
GB1009984A (en) * 1961-12-14 1965-11-17 Saunders Valve Co Ltd Fluid controlling valves
JPS5244439U (de) * 1975-09-25 1977-03-29
IT1138189B (it) * 1981-09-02 1986-09-17 Nuovo Pignone Spa Guarnizione anulare di tenuta per valvola a sfera di intercettazione
JPH0720457Y2 (ja) * 1986-12-09 1995-05-15 株式会社竹中工務店 切替、流量調節機能を有する電動式ボール弁
CN1018664B (zh) * 1988-11-02 1992-10-14 姜树忠 搪玻璃跟踪球阀
JPH1038102A (ja) * 1996-07-19 1998-02-13 Saginomiya Seisakusho Inc ４モード切換弁
US6974121B2 (en) 2002-03-19 2005-12-13 Fisher Controls International, Inc. Fluid flow control valve with bi-directional shutoff
DE102009020186B4 (de) 2009-05-06 2011-07-14 Audi Ag, 85057 Ausfallsicherer Drehsteller für einen Kühlmittelkreislauf
US8979068B2 (en) * 2011-02-11 2015-03-17 Yeary & Associates, Inc. Differential pressure sealing device for ball valves
JP5806871B2 (ja) 2011-07-27 2015-11-10 株式会社ケーヒン 弁装置
DE102013222825A1 (de) * 2013-11-11 2015-05-13 Schaeffler Technologies Gmbh & Co. Kg Einzellagerung einer Drehschieberwelle mit reduziertem Radialspiel und angepasster Führungslänge
DE102014206529A1 (de) * 2014-04-04 2015-10-08 Schaeffler Technologies AG & Co. KG Wärmemanagementmodul mit Drehschiebertechnologie
JP6327401B2 (ja) * 2015-06-09 2018-05-23 株式会社デンソー 減圧弁

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
US20170211460A1 (en) 2017-07-27
EP3199848A1 (de) 2017-08-02
CN107023375A (zh) 2017-08-08
US10513966B2 (en) 2019-12-24
JP6668780B2 (ja) 2020-03-18
JP2017133547A (ja) 2017-08-03

Similar Documents

Publication Publication Date Title
EP3199848B1 (de) Kühlmittelsteuerventilvorrichtung
US10280829B2 (en) Flow rate control valve
EP3232099B1 (de) Kühlmittelsteuerventilvorrichtung
JP6616142B2 (ja) 流量制御弁
JP2017003064A (ja) 流量制御弁
US10626784B2 (en) Rotary type valve device
US11149627B2 (en) Cooling-water control valve device
WO2017057062A1 (ja) 冷媒制御バルブ装置
JP2016188693A (ja) 冷媒制御バルブ装置
CN116181472A (zh) 阀装置
US11821536B2 (en) Valve device
CN109611573B (zh) 球阀几何形状和动态密封组件
US11162601B2 (en) Valve device
JP2017020424A (ja) エンジンの冷却液制御バルブ装置
CN112780802B (zh) 阀装置
US11079020B2 (en) Seal ring and seal structure
US10704455B2 (en) Rotary type valve device
JP2020159514A (ja) 制御バルブ
WO2016006175A1 (ja) バルブ装置
CN114060570A (zh) 旋转式阀装置
CN116221452A (zh) 旋转式阀装置
JPH09287522A (ja) 内燃機関の吸気装置

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20170310

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

RIC1 Information provided on ipc code assigned before grant

Ipc: F16K 11/087 20060101ALI20190813BHEP

Ipc: F16K 5/06 20060101AFI20190813BHEP

Ipc: F01P 7/14 20060101ALI20190813BHEP

Ipc: F25B 41/06 20060101ALI20190813BHEP

Ipc: F01P 7/16 20060101ALI20190813BHEP

Ipc: F16K 5/20 20060101ALI20190813BHEP

INTG Intention to grant announced

Effective date: 20190909

RIN1 Information on inventor provided before grant (corrected)

Inventor name: MARUYAMA, KOICHI

Inventor name: SUZUKI, HIDEYUKI

Inventor name: KOGA, YOJIRO

Inventor name: MATSUSAKA, MASANOBU

Inventor name: YUMISASHI, NAOTO

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602017011817

Country of ref document: DE

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1235348

Country of ref document: AT

Kind code of ref document: T

Effective date: 20200315

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20200219

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200519

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200219

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200219

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200219

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200219

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200219

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200520

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200519

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200619

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200219

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200219

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200219

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200219

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200219

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200219

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200712

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200219

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200219

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200219

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1235348

Country of ref document: AT

Kind code of ref document: T

Effective date: 20200219

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602017011817

Country of ref document: DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20201120

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200219

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200219

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200219

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200219

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602017011817

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200219

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20210125

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210125

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20210131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210803

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210131

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210125

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210125

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20170125

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200219

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200219